Cutoff and transfer mechanism for rewinder



March 3, 1970 J. J. BRADLEY CUTOFF AND TRANSFER MECHANISM FOR REWINDER Filed July 24., 1968 3 Sheets-Sheet 1 INVENTOR. lOHN J. BRADLEY fi I ATT'YS Mg March 3, 1970 J. J. BRADLEY CUTOFF AND TRANSFER MECHANISM FOR REWINDER Filed July 24, 1968 3 Sheets-Sheet 2 I ll-I11 4=ill ll/A in!!! |i!|.]i 0E. 3 mm m hm wn n 1 h c i .I 2 Q B 6 mv M m 3 mm mm mm LE: i mm N v Om NW mm ow Q mm NV m m 0 mm 6 Q 5 mm mv v voz 1i. .li mm; s \F \f INVENTOR:

JOHN J. BRADLEY March 3, 1970 J. J. BRADLEY CUTOFF AND TRANSFER MECHANISM FOR REWINDER 3 Sheets-Sheet 5 Filed July 24, 1968 INVENTOR. JOHN J. BRADLEY BY United States Patent O 3,498,558 CUTOFF AND TRANSFER MECHANISM FORREWINDER John J. Bradley, Green Bay, Wis., assignor to Paper Converting Machine Company, Inc., Green Bay, Wis., a corporation of Wisconsin Filed July 24, 1968, Ser. No. 747,138 Int. Cl. B65l1 19/26 US. Cl. 24256.8 4 Claims ABSTRACT OF THE DISCLOSURE BACKGROUND AND SUMMARY OF INVENTION Heretofore rather elaborate cutoff and transfer mechanisms have been employed in conjunction with rewinders. In most instances, these were associated with a cutoff bed roll and required the use of a projectable knife. In contrast to the bed roll type of cutoff (which is exemplified by Patents 2,769,600 and 3,179,348) I employ a knifeless snubber roll which because of its arrangement in operation literally snaps the web transversely while simultaneously urging it against a glue equipped core on a mandrel just entering the winding station of the rewinder.

An important advantage of this arrangement is that it permits the necessary timing facilities to be located at a point somewhat remote from the cutoff action, thereby simplifying the construction and maintenance of the machine.

DETAILED DESCRIPTION The invention is explained in conjunction with an illustrative embodiment in the accompanying drawing, in which:

FIG. 1 is a fragmentary side elevational view of certain operational parts of a rewinder and which includes the novel cutoff and transfer mechanism;

FIG. 2 is a view similar to FIG. 1 but of only a portion thereof and showing the snubber roll in its cutoff and transfer position;

FIG. 3 is a generally longitudinal sectional view of a portion of the machine corresponding generally to a view taken along the sight line 33 applied to FIG. 1;

FIG. 4 is another generally longitudinal sectional view of the machine and corresponds essentially to a view taken along the sight line 44; and

FIG. 5 is a perspective view of the machine.

In the illustration given and with reference to FIGS. 1 and 4, the numeral designates generally the frame of the machine. It will be appreciated that rewinders commonly employ'a pair of side frames which for the most part are identical. In FIG. 1, only the frame for the far side is seen so as to present in unobscured fashion the various rolls that are supported between the side frames 10 and 10a (see FIGS. 3-5).

I have employed certain symbols, i.e., letters, for nonmachine parts and which are helpful in understanding the operation of the inventive machine. For example, the symbol W designates the web which travels through the machine winding up in a web roll R being wound one.

3,498,558 Patented Mar. 3, 1970 core C. In FIG. 2, the almost complete web roll is designated by the symbol R and it is seen that the web roll R has a tail T which ultimately will be glued to the web roll itself.

In FIG. .2, the web is seen to be severed to provide the tail T and at the same time a reverse fold F shown in the process of being picked up by the core C for winding thereon.

At the extreme left-hand portion of FIG. 1, the web W is seen to be passed between embossing rolls 11 and 12. It is to be understood that embossment of the Web is optional. Thereafter, the web passes over and travels with a perforating bed roll 13 associated with a shear-cut perforating mechanism 14. Details of this construction can be seen in Patent 2,870,840. Thereafter the web pases around a detour or direction changing roll 15, being in partial wrapping engagement therewith. Proceeding further to the right of FIG. 1, it is seen that the web W passes over a detour 'bar 16 for winding on the mandrel 17. The mandrel 17 is approaching the end of the winding station, i.e., the upper left-hand quadrant of the travel of turret 19 while the mandrel 18 is just about to enter the winding station. Thus, the turret 19 travels through degrees for each web roll or count in the parlance of the trade.

The numeral 20 designates generally the snubber roll refered to previously and which constitutes an important part of the transfer and cutoff mechanism. The snubber roll 20 is shown in FIG. 1 in the position that it occupies during the winding cycle and in FIG. 2 as at 20' in the position that it occupies during cutoff and transfer. For oscillating the snubber roll over a minor arc, it is mounted on a rocker arm 21. The rocker arm 21 is pivoted on the same shaft that carries the detour roll 15 and the rocker arm 21 carries a lug or ear 22 to pro vide a connection for a connecting rod 23. As indicated in FIG. 2, the movement of the connecting rod 23 results in the oscillation of the snubber roll 20. It will be appreciated that two assemblies 21-23 are provided, one for each side of the machine, as will be brought out more clearly hereinafter with reference to FIG. 3.

The numerals 25 and 26 designate other mandrels in FIG. 1 and the numerals 27-29 designate other detour bars. As can be appreciated from a consideration of FIG. 4, the detour bars (as at 29) serve to stiffen and reinforce the turret 19. I

In FIG. 4, the numeral 30 designates the turret drive while the numeral 31 designates generally the mandrel drive. It will be appreciated that the mandrels rotate at relatively high speed during the winding even while being orbite'd by virtue of the slower rotation of the turret.

Turning now to FIG. 3, the numeral 32 (at the extreme bottom) designates the principal drive shaft for the machine. It will be appreciated that power take-offs are provided at a number of places but these are omitted for the clarity of presentation. The main power input is delivered to the shaft 33 which provides the mounting for the perforating bed roll 13. A train of gears 34 is employed for connecting the shaft 33 with the detour roll 15. In similar fashion another train of gears generally designated 35 couple the detour roll 15 with the snubber roll 20. Thus, the rotation of the snubber roll 20 can be precisely synchronized with the rotation of the perforating bed roll 13.

In FIG. 3 and just to the right of the perforating bed roll 13 is provided a pivot shaft 36. In accordance with conventional practice, the rolls for the most part or journaled between the side frames 10 and 10a and again, for the sake of simplicity of presentation, reference to various mountings, bearings, etc. has been omitted. The pivot or rocker shaft 36 is equipped with a pair of arms 37. As can be seen relative to the upper one of the arms 37, this provides a pivotal connection for the connecting rod 23. Thus, as the pivot shaft 36 rocks or oscillates, so also will the snubber roll 20.

For the most part, the remainder of the detailed description is concerned with the upper left-hand corner of FIG. 3 which has to do with the mechanism employed to power the pivot shaft 36.

The numeral 38 designates a gear fixed to the perforatingbed roll shaft 33adjacent the end 39 remote from the main power input 32. The gear 38 is meshed with a driven gear 40 mounted on a shaft 41 provided in suitable mounting on the frame. The shaft 41 in effect is an intermediate or transfer shaft. The shaft 41 in turn carries a gear 42 which is coupled to a gear 43 fixed on yet another intermediate shaft 44. Continuing with the power train, the shaft 44 is equipped with a gear 45 which is coupled to a gear 46 fixed to the actuator shaft 47. The gear 46 constitutes an important replaceable gear in the power train embodying the elements 38-47 just described, being used to establish the relationship of the speed of the cams used to oscillate the pivot shaft 36 with the speed of the perforating bed roll 13. I choose to designate this gear 46 as a count change gear so that when the size of the web roll R changes (as from 200 to 500 squares), the gear 46 is changed accordingly.

The numeral 48 designates generally a cam which is fixed to the shaft 47 and which is the actuator or indexing cam for the pivot shaft 36. For this purpose, the pivot shaft 36 is equipped with a cam follower arm carrying a cam follower 49.

I control more effectively the operation of the mechanism by employing a lock out cam 51. This cam 51 operates at a speed considerably slower than the actuator cam 48 and serves to prevent actuation of the pivot shaft 36 until the desired point in the cycle. Thus, the cam 48 can rotate much faster than would be possible if it had to actuate the pivot shaft once each cam revolution.

The lock out cam 51 operates against a cam follower 52 mounted on the same arm 50 as the cam follower 49. As seen in FIG. 1, the cam follower 52 may move into the cam slot 51' to the maximum position 52', thereby enabling the cam follower 49 to follow the contour 48'. The lock out cam 51 is coupled to a gear 53 which is driven by a gear 54 fixed to an intermediate drive shaft 55. The drive shaft 55 in turn is powered through gears 56 and 57, the latter being fixed to the actuator shaft 47.

The pivot shaft .36 also provides a bearing for a tail seal actuator 58 which is powered also from the gear 53to oscillate the roll 59 (see FIGS. 1 and 5). For this purpose, a cam 60 associated with the lock out cam 51 is provided that operates against a cam follower 61 provided on the actuator 58. Not shown is the connecting rod between the actuator 58 and the tail seal roll 59. As can be appreciated from FIG. 5, the roll 59 may be pivoted in a fashion analogous to the snubber roll 20to apply glue through the fingers 62.

In the operation of the machine which is depicted schematically in FIGS. 1 and 2, the four detour bars 16 and 27-29 are so positioned that when the web is being wound on a mandrel at twelve oclock, i.e., the mandrel 17, the web is spaced just slightly from the mandrel at nine oclock, i.e., the mandrel 18. The mandrel 18 has ensleeved thereon a glue-equippedcore C so as to be ready for the transfer depicted in FIG. 2. Themachine depicted in FIG. 5 is semi-automatic, requiring manual help for removing and replacing the mandrels. The wound core equipped mandrel is detached from the turret 19 and placed on a roll removing mechanism 63, a spare mandrel is seen at 64. I

As the final count is reached, the snubber roll 20 is oscillated towardthe mandrel 18 just entering the winding station and is seen to be rotating in a direction opposite that of the direction of web travel, i.e., the snubber roll rotates or turns against the web travel. As the end of the winding cycle is approached, the snubber roll is lowered slowly under the dictation or control of the contour of the actuator cam 48. This dropping of the snubber roll 20 continues until the resilient pad 24 just misses the web, i.e., passes by the mandrel 18. Once the pad or snubber 24 is passed the mandrel 18, the snubber roll 20 continues to move toward the mandrel 18 so that during the next revolution of the snubber roll 20 the pad 24 pushes the web W against the core C on the mandrel 18. Because the rotation of the snubber roll 20'is timed in synchronism with the perforating bed roll 13, this snubbing action occurs when a transverse perforationlies between the new core C (on the mandrel 18) and the detour bar 16. The web is thus supported at two relatively close points with a perforation therebetween. The snubber or pad 24 restrains the web from advancing While the mandrel 17 continues to advance the web, these opposing forces resulting in a snap of the web at the perforation' which has been designated P in FIG. 1. Thus, a precise count with a straight across cutoff is achieved. By the same token, the web is caused to be wound on a counterclockwise rotating mandrel and develops an advantageous reverse fold as at F. This is especially advantageous when multi-ply webs are being wound since the uppermost web is confined in a pocket developed by the reverse fold.

Through the use of gearing and essentially a single cam arrangement, a precise and reliable operation is achieved without the need of going to the complicated bed rolls heretofore employed in conjunction with cutoff and transfer.

While in the foregoing specification a detailed description of an embodiment of the invention has been set down for the purpose of explanation, many variations of the details herein given may be made by those skilled in the art without departing fr m the spirit and scope of the invention.

I claim:

1. In a rewinder for flexible webs, a frame, a turret rotatably mounted on said frame and carrying a plurality of mandrels rotatably mounted thereon, means associated with said frame for rotating said turret to sequen tially orbit said mandrels through a winding station, means associated with said frame for rotating said mandrels to wind said web thereon into rolls of predetermined size, means on said frame for advancing said web toward said winding station and including a perforator to transversely perforate said Web, an improved cutoff and transfer mechanism on said frame interposed between said perforator and a mandrel on which said web is being wound in said winding station characterized by the fact that it includes:

a snubber roll mounted for both rotary and oscillatory movement on said frame, means coupling said snubber roll and perforator for synchronizing the rotation of said snubber roll with the perforation of the perforator, means on said frame for oscillating said snubber roll at a predetermined time in the cycle of winding each web roll, said oscillating means moving said snubber roll to urge said web against a mandrel equipped with a core having glue on its Outer surface and next to be wound with said web while the surface of the snubber roll about to contact said web and the adjacent surface of said core are both moving in a direction opposite to the direction of web travel whereby said web is substantially simultaneously severed along a transverse perforation and urged against said glue surface. 2. The rewinder of claim 1 in which said turret is equipped with a plurality of detour bars, a detour bar being positioned between each of adjacent mandrels, each detour bar having the characteristic of supporting the web being wound away from the surface of a mandrel about to enter said winding station until the web is engaged by said snubber rollated with the previously mentioned cam for determining 10 the time in the winding cycle when the snubber roll oscillation occurs.

References Cited UNITED STATES PATENTS Schultz et al. 24256 Christman 24256.8 Corbin et al 2425 6.8 Kohler et al. 24256 Nelson 24256 Turner et al. 24256 Jacobs et al. 24256 STANLEY N. GILREATH, Primary Examiner W. H. SCHROEDER, Assistant Examiner 

